Compensator



Feb. 2 1926. 1,571,57 7

J. M. DAYTON 61H07 new Feb. 2, 1926.

J. M. DAYTON COMPENSATOR AFiled August 18 1925 2 Sheets-Sheet 2 PatentedFeb. 2, 1926.

UNITED STATES PATENT OFFICE.

JAMES M. DAYTON, OF HARTFORD, CONNECTICUT, ASSIGNOR TO THE DAYTON MANU-FACTURING COMPANY, OF TORRINGTON, CONNECTICUT, A CORPORATION OF CON-NECTICUT.

COMPENSATOR.

Application filed August 18, 1925.

To 1M whom t may concern:

Be it known that I, JAMns'M. DAYTON, a citizen of the United States,residing at Hartford, in thc county of Hartford, State of Connecticut,have invented certain new and useful Improvements in Con'ipensators, ofwhich the following is a description, reference being had to theaccompanying drawing and to the figures of reference marked thereon.

This invention relates to improvements 1n mechanical movements forconverting an angular displacement of one element into a differentangular displacement of another r element journalled coaxially with thefirst,

and is particularly applicable to the counting train of gasolinedispensing apparatus.

Heretofore, when counters were applied to pumps, it has been founddifficult to obtain an accurate registration of the number of gallonsdelivered by the pump. The pump cylinders have been made of drawntubing, and were never of an exact diameter. The amount delivered by thepump could be regulated by an adjustable stop which limited the movementof the piston, so that the volume discharged was constant from allpumps. Since, however, the movement of the piston determined therotation of the counter, obviously with a greater cylinder diameter anda correspondingly shorter stroke, the registration was less. It has beenproposed to so dispose the counter that it is only acted upon atintervals, and thus f by regulation of the intervals obtain aregistration in steps: this system is subject to the disadvantage that adishonest employee can work kthe pump between the stops defining theintervals to obtain a flow of gasoline which is not registered on thecounter. n

The present invention proposes a mechanical movement to be connectedbetween the crank handle of the pump and the counter, by which the twoare at all times positively connected so long as gasoline is beingdrawn. The variation in length of strokes between different calibratedpumps is taken care of by a variation in the distance traveled betweendifferent parts of the driving mechanism, and particularly between twocoaxiallv journalled elements.

While the invention will be described and illustrated as applied to algasoline dispens- Serial No. 50,974.

ing pump, it will be understood.`y that it may be applied to anystructure where it is.

desired to obtain a constant distance of rota'- tion from a movement ofconstant but arbiof the elements of the pump, compensator`- and counter.

Figs. 3, 4 and 5 are diagrams of the relative positions of the gears andpinion of the compensator.

The driving mechanism is contained within a framework consisting of theplates 10, 11. and the spacing posts 12, 13. The shaft 14 is driven byany appropriate means from the crank shaft of the pump, so that therotation of shaft 14 is positive and at all times follows the movementsof the pump piston. Mounted on the shaft 14 within the framework is apinion 15 which meshes with a large gearwheel 16 which is looselymounted on a stud 17 fixed to the framework.

An arm 18 is likewise mounted on the stud 17 for free movement withregard thereto, and is riveted at 19 to the gear 16 so as to partake inthe movements of the latter, and move therewith through the same angleabout the axis of the stud 17. The outer end of this arm 18 has anaperture to receive the reduced portion 20 of a pinion 2 1; a holdingwasher 22 and a cotter pin 23 hold the pinion in position in regard tothe arm 18.

A compensated gear 24 preferably of the same diameter and number ofteeth as the gear 16 is mounted on the end of the stud 17, which has anenlarged head 25 to prevent the separation of the various elementsthereon. This gear meshes with the pinion 21 and with a driven gear 26which is connected by a shaft 27 with one side of a ball clutch 28.rlhis clutchmay be constructed in any manner, and since a peculiarconstruction thereof is no part of my present invention, vit is.sufficient to state that itsv function' is to positively couple thecrank handle motion with the counter 39 duringthe operation of pumpingout gasoline, and to release such coupling during travel of the handlein the opposite direction, when. the pump is sucking gasoline for thenext delivery. In this way the counter 89 is always driven in a singledirection, and adds up the successive movements in such direction, nomatter how small.

The compensating device is to provide a possible variation in theangular displacements of the positively coupled gears 16 and 24. It thepinion 21 were locked with regard to the gear 16, the gear 24 would be'driven at the identical speed of the latter. To obtain a compensationbetween the movements of the shafts 14 and 27 which will take care ofthe diiferences in piston strokes, it is necessary that the gear 21advance the gear 24 either faster or slower than the gear 16, as thecase may be.

For this purpose a sliding carriage 2S) is mounted in a slotted guideway30 on the frame plate 11. A screw 31 with head 31a is rotatablyjournalled in an ear 32 fastened to this plate 11, and engages in thiscarriage 29, so that by rotation of the screw 31, the carriage may bemoved closer to or farther from the axis of the stud 17. The carriagesupports therein an arm by an end 33a serving as a pivot about an axisparallel to that ot the stud 17, but having its longer portion 33 bentat right angles and passed through an aperture` formed 1n the pinion 21for sliding movement therein.

Vhile the various parts may be given any desired sizes appropriate tothe purpose for which employed, it is preferred for gasoline dispensingdevices in which seven turns of the pump handle 40 rotates the gear 15for a full revolution to give the gear 15 twelve teeth, gear 16forty-eight teeth, gear 24 forty-eight teeth, pinions 26 and 21 twelveteeth each. Under such conditions, a normal pump cylinder 41 whichrequires exactly seven turns of the pump handle to deliver ten gallonsof gasoline, will cause a full revolution of gear 15 during thisdelivery, and therewith a,y rotation of gear 16 through 90 degrees: thisshould be transmitted to pinion 26 as a full revolution, which throughthe ball clutch 28 drives the counter for a full revolution andregisters ten upon the tot-alizing wheels of the latter. Obviously toobtain an exact revolution ot the pinion 26, the gear 24 must rotate bytwelve teeth or 90. In this case, therefore, the two gears 16 and 24turn together: Which'condition is obtained if pinion 22 has no relativerotation but is merely translated by the arm 18. For this purpose thepivot point of arm 33 must coincide with the axis of the stud shaft 17,and is adjusted to such position by the screw 31.

l For a second case, however, assume that the device is applied to apump `vvhose cylinder diameter is such that eight turns of the pumphandle are necessary to deliver ten gallons of gasoline. This will causea rotation of gear 15 through more than one revolution, and will rotategear 16 through, say, 103 degrees. Since pinion 26 and gear 24 meshtogether, and must only turn through the same angle as before (90degrees for gear 24) to register the ten gallons delivered; it isnecessary that the 103 dogree displacement of gear 16 should cause a 90degree displacement of gear 24. For this purpose, the ypivot point ofarm 33 must be displaced so that the pinion 21 will revolve sufficientlyduring its translation by arm 18 about the axis ot shaft 17 to reducethe total rotation of gear 24 to exactly 90 degrees. This may beaccomplished by rotation of the adjusting screw 31.

Mathematically, the gear 15 will be rotated, say, through 13% toothdivisions: and gear 16 through the same peripheral distance. Sincehowever gear 24 must onlv rotate through 90 degrees or 12 toothdivisions, it is clear that pinion 21 must lose 13?- minus 12 or 11;tooth divisions, which on a twelve tooth pinion is t ot a circumferenceor about 51 degrees, as represented by the angle between lines a and ain Fig. 5. This angle is derived according to Figs. 3, 4 and 5, asfollows: In Fig. 3, which may be designated the initial position of theparts, it the pump handle 40 he turned to deliver gasoline or otherliquid, the pinion 21 is carried upon the arm 18 counterclockwise aboutthe axis 17. It the line joining the centers of the pinion 21 and otpivoting portion 38" ot the arm 33 be designated ain all figures, andthe line joining` the axes of the pinion 2l and the gears 16, 24 bedesignated as a," in Fig. 3: then as the pinion is carriedcounterclockwise around the axis 17, the pinion is caused to rock, withfirst a shortening and then a lengthening of the distance between thecenters of arm 33 and pinion 21 in the example illustrated, so that thegear 24 has a lesser rotation than the armi 18. During this rocking ofthe pinion 21 upon the gear 24, the line of centers a in Fig. 3, becomescoincident with line a in Fig. 4, and passes to become line a in Fig. 5.As shown this angle between lines a and a. is about 51 degrees, butobviously may he made greater or 'smaller by changing the distancebetween the centers of arm 33 and the axis 17. During this rocking ofthe pinion 21 with regard to the gear 24, the latter is thus given aretrograde movement with respect to the gear 16 (or a lesser rotationwith regard to the frame) of 1? tooth divisions, which just corrects thesystem.

The method preferably employed for adjustment of the mechanism is asfollows: The pump 41 is calibrated and adjusted until it deliversexactly ten gallons. This may be done in any suitable manner, such asregulation of the lengthwise movement of the rack R by means of theadjusting screw S while pumping a liquid, until the. delivery is therequired amount: this screw S is mounted on some part of the frame F,and has a lock nut L to preserve its adjustment when made.l The countingmechanism is attached, and the pump handle turned as though pumping tengallons. The gear 16 will in this manner be turned through some anglenear 90 degrees. The screw 31 is then rotated until the gear 24 liesexactly 90 degi'ees away from its original position. Since 90 degrees ofmovement of gear 24 represents one revolution of the counter shaft, theapparatus is now adjusted to the particular pump, and is locked at thisadjustment.

It is apparent that movements of the, pump handle less than thatrequired t0 deliver ten gallons will produce corresponding revolutionsof gears 15 and 16 and of arm 18. The compensation by pinion 21 and arm33 will be substantially correct for any fi'actional delivery. Thesesmall fractions will be added by means of the ball clutch, no matter howminute they may be.

Obvious modifications in the sizes and relations of the several partsmay be made to adapt them to their employment within the scope of theappended claims.

I claim:

1. In a liquid dispensing device, a pump having an arbitrary length ofstroke for a given volume of delivery, an arm, means to rock said armthrough an angle proportionate to the length of stroke of said pump, apinion carried by said arm, a gear driven by said pinion and mountedco-axially with the fulcrum of said arm, means to impose upon saidpinion a movement of revolution during its translation about said gear,said gear receiving a rotation in proportion to said revolution andtranslation, and means to sum up the movements of said gear in onedirection.

2. In a gasoline dispensing device, a pump having an arbitrary`length ofstroke for a given volume of delivery, a frame, a pair of gears mountedfor loose coaxial rotation in said frame, means to positively drive onegear in proportion to the movement of said pump, a pinion carried bysaid dr1ven gear and in mesh with the second gear, means to impose uponsaid pinion a movement during the rotation of said driven gear, saidmovement and said rotation determining the angle of rotation of saidsecond gear, a counter driven from said second gear during the movementof the latter in one direction, and means to release said counter fromsaid second gear during the rotation of the latter in the reversedirection.

3. In a compensating device for transmitting as uniform actuations of 'acounter the dierentlarbitrary length of stroke of any one of a number ofliquid dispensing pumps which deliver calibrated equal volumes duringsuch individual Varbitrary length of stroke, a frame, an arm pivoted onsaid frame, means to rock said arm from one of said pumps and inproportion to its length of stroke, a rod fulcrumed on said frame, meanswhereby said aim Will rock said rod about its fulcriim, means slidablycarried by said rod to actuate said counter, and means to shift thefulcriim 0f said rod to attain a uniform actuation of said counter for agiven volume of delivery when said device is applied to any of saidpumps,

4. In a compensating devicel for transmittingas uniform actuations of acounter the diti'erent arbitrary length of stroke of any oiie of anumber of liquid dispensing pumps which deliver calibrated equal volumesduring such individual arbitrary length of stroke, a fulcrumed arm,means actuated from one of said pumps and in accordance with themovement thereof to rock said arm, a pinion carried by said arm, adriven gear meshing with said pinion, a rod sliding in said pinion andhaving a rocking movement `about a relatively fixed pivot, and means tovary the position of said pivot relative to the fulcrum of the arm toestablish the coinpensation for the pump to which the device isattached.

5. In a compensating device for transmitting as uniform actuations of acounter the different arbitrary length of stroke of any one of a numberof liquid dispensing pumps Which deliver calibrated equal volumes duringsuch individual arbitrary length of stroke, a first and second membermounted eoaxially With regard to each other, a pinion carried by one ofsaid members and in mesh with the other, a pivot, a rod mounted on saidpivot and sliding in a transverse aperture of said pinion and fixing aninvariable radial directive relation of said aperture and saidl pivot,and means to move said pivot relative to the common axis of saidmembers, whereby said pinion causes a relative difference of angularmovement between said members dependent upon its relative revolution asdetermined by said rod.

6. In a compensating device for transmitting as uniform actuations of acounter thc different arbitrary lengths of stroke of any one of a numberof liquid dispensing pumps which deliver calibrated equal volumes duringsuch individual arbitrary length of stroke, a frame, a first memberpivoted on said frame, a mechanism actuated from said pump to move saidfirst member in accordance with the length of stroke of said pump, asecond member pivoted on said frame, means to connect said second memberto said counter to actuate the same, a lever pivoted on said frame, atransmitting element driven by said first member and drivingsaid secondmember and during the transmitting movement sliding upon said lever, andmeans to adjust the pivot point of said lever.

7. In a liquid dispensing device, a pump having an arbitrary length ofstroke for a given volume of delivery, a frame, a driver gear, means torotate said driver gear in accordance With the movement of said pump, aVdriven gear in mesh with said driver gear, an arm mounted coaxially withand driven positively bv said driven gear, a compensated gear looselymounted coaxially with said driven gear` a pinion carried by said arm inmesh with said compensated gear, a compensator rod slidably mounted in atransverse aperture of said pinion. a relatively stationary pivot forsaid compensator rod attached to the frame, means to adjust said pivotlinearly relative to the axis of said driven gear and to and from theaxis of said, pinion, a second driven gear in mesn with said compensatedgear and driven therefrom, a counter, a clutch, and means to connectsaid second driven gear, said counter and said clutch whereby saidsecond driven gear drives said counter through said clutch in onedirection, and rotates freely thereof in the opposite direction.

8. The combination of a counting mechanism for a pump, a continuouslyoscillating lever actuated with the pump, a second oscillating lever inoperative relation tvith the counting mechanlsm, a fixed fulcrum forsaid second lever in fixed relation thereto, said second lever beingactuated directly by said first lever, and means to adjust said fixedfulcrum and said second lever.

9. The combination of a counting mechanism for a pump. a continuouslyoscillating lever actuated with the pump, a second oseillating lever inoperative relation With the counting mechanism, a fixed fulcrum for saidsecond lever in fixed relation there to, and mechanism whereby said irstlever oscillates said second. lever at continuously varying distancesfrom said fulcrum, and means to adjust said fixed fulcrum and saidsecond lever.

10. The combination of a counting mechanism for a pump, a frame, acontinuously oscillating lever actuated with the pump, a pivot for saidfirst lever mounted on said frame, a second oscillating lever inoperative relation with the counting mechanism, a fulcrum on said framefor said second lever, said second lever being actuated directly by saidfirst lever, and means to adjust. the position of said fulcrum withregard to said pivot.

In testimony whereof, I aiiix my signature. i

JAMES M. DAYTON,

